EP2597343B1 - Électrovanne - Google Patents

Électrovanne Download PDF

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Publication number
EP2597343B1
EP2597343B1 EP20110190645 EP11190645A EP2597343B1 EP 2597343 B1 EP2597343 B1 EP 2597343B1 EP 20110190645 EP20110190645 EP 20110190645 EP 11190645 A EP11190645 A EP 11190645A EP 2597343 B1 EP2597343 B1 EP 2597343B1
Authority
EP
European Patent Office
Prior art keywords
mouth
open
solenoid valve
close element
fluid
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP20110190645
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German (de)
English (en)
Other versions
EP2597343A1 (fr
Inventor
Sergio Stucchi
Onofrio De Michele
Raffaele Ricco
Marcello Gargano
Chiara Altamura
Carlo Mazzarella
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Centro Ricerche Fiat SCpA
Original Assignee
Centro Ricerche Fiat SCpA
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Priority to EP20110190645 priority Critical patent/EP2597343B1/fr
Priority to US13/591,816 priority patent/US8851118B2/en
Publication of EP2597343A1 publication Critical patent/EP2597343A1/fr
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Publication of EP2597343B1 publication Critical patent/EP2597343B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F16K31/0603—Multiple-way valves
    • F16K31/0624—Lift valves
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/36—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition including a pilot valve responding to an electromagnetic force
    • B60T8/3615—Electromagnetic valves specially adapted for anti-lock brake and traction control systems
    • B60T8/363—Electromagnetic valves specially adapted for anti-lock brake and traction control systems in hydraulic systems
    • B60T8/364—Electromagnetic valves specially adapted for anti-lock brake and traction control systems in hydraulic systems switching between a number of discrete positions as a function of the applied signal, e.g. 3/3-valves
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/86582—Pilot-actuated
    • Y10T137/86614—Electric

Definitions

  • the present disclosure relates to a solenoid valve, in particular of the type comprising three mouths and three operating positions, wherein the three mouths comprise:
  • valves with three mouths and three operating positions are known whereby a fluid communication between an inlet mouth and two outlet mouths is selectively set up in order to direct alternatively the fluid towards one of the aforesaid outlet mouths or to both of them.
  • the term "operating position" is intended to indicate a condition of operation of the solenoid valve in which assigned to one or more moving elements of the solenoid valve itself is a position that results, amongst other things, in a particular mode of connection of the operating mouths of the solenoid valve.
  • the environments giving out into which are the inlet and outlet mouths have pressure values different from one another, where the maximum value of pressure impinges on the inlet mouth, whereas impinging on the outlet mouths are two different levels of pressure, which are both lower than the pressure that impinges on the inlet mouth.
  • Switching of the solenoid valve can be exploited to modulate the level of pressure in a load connected to the inlet mouth.
  • the different levels of pressure of the environments connected to the mouths of the solenoid valve determine the modulus of the resultant of the pressure forces acting on the moving elements of the solenoid valve itself, in particular in the axial direction.
  • the electromagnet must consequently be sized in such a way as to be able to actuate the moving elements even when the resultant of the pressure forces assumes a maximum value.
  • the object of the present invention is to provide a solenoid valve comprising three mouths and three operating positions that will be able to work in three environments at pressures that differ from one another and with marked pressure swings between them, where actuation of moving elements of the solenoid valve will be substantially irrespective of the levels of pressure in the environments connected to the mouths of the valve itself, and where moreover the solenoid valve will be able to process high flows of fluid and will be characterized by extremely contained switching times.
  • a solenoid valve having all the characteristics listed at the start of the present description and further characterized in that it comprises a first open/close element and a second open/close element, co-operating with a first contrast seat and a second contrast seat, respectively, wherein the first open/close element and the first contrast seat are provided for regulation of the passage of fluid from the first mouth to the third mouth, wherein the second open/close element and the second contrast seat are provided for controlling the passage of fluid from the first mouth to the second mouth, the solenoid valve being moreover characterized in that the electromagnet can be actuated for impressing on the second open/close element:
  • the reference number 1 designates as a whole a solenoid valve according to a preferred embodiment of the invention.
  • the solenoid valve 1 comprises a first mouth 2 for inlet of a working fluid, and a second mouth 4 and a third mouth 6 for outlet of said working fluid.
  • the working fluid is oil, but the solenoid valve 1 can work in the same way with other liquids or with gaseous fluids.
  • the solenoid valve 1 comprises three operating positions designated by the references P1, P2, P3.
  • An electromagnet 8 comprising a solenoid 8a can be controlled for causing a switching of the operating positions P1, P2, P3 of the solenoid valve 1, as will be described in detail hereinafter.
  • the dashed segments connecting the mouths 2, 4 and 6 indicate schematically the leakages of liquid (in particular oil) through the dynamic seals provided between the moving components: said leakages (hydraulic consumption of the valve) come out of the mouth that is at a lower pressure.
  • the solenoid valve 1 comprises a plurality of components coaxial to one another and sharing a main axis H.
  • the solenoid valve 1 comprises a jacket 10, housed in which are a first open/close element 12 and a second open/close element 14 and the electromagnet 8 containing the solenoid 8a.
  • the jacket 10 is traversed by a through hole sharing the axis H and comprising a first stretch 16 having a first diameter D16 and a second stretch 18 comprising a diameter D18, where the diameter D18 is greater than the diameter D16. At the interface between the two holes there is thus created a shoulder 19.
  • the mouths 2, 6 are provided by means of through holes with radial orientation provided, respectively, in a position corresponding to the stretch 16 and to the stretch 18 and in communication therewith.
  • first annular groove 20 a first annular groove 20, a second annular groove 22, and a third annular groove 24, each of which are designed to receive a gasket of an O-ring type, arranged on opposite sides with respect to the radial holes that define the mouth 2 and to the radial holes that define the mouth 6.
  • the mouth 6 is comprised between the grooves 20 and 22, whereas the mouth 2 is comprised between the grooves 22 and 24.
  • the three annular grooves 20, 22, 24 are provided with the same seal diameter so as to minimize the unbalancing induced by the resultant of the pressure forces acting on the outer surface of the jacket 10, which otherwise would be such as to jeopardize fixing of the jacket of the solenoid valve in the corresponding seat provided on a component or in an oleodynamic circuit where it is installed.
  • the first open/close element 12 is basically configured as a hollow tubular element comprising a stem 26 - which is hollow and provided in which is a first cylindrical recess 27 -, a neck 28, and a head 30, which has a conical contrast surface 32 and a collar 34.
  • the neck 28 has a diameter smaller than that of the stem 26.
  • a ring of axial holes 34A preferably provided in the collar 34 is a ring of axial holes 34A, whilst a second cylindrical recess 35 having a diameter D35 is provided in the head 30.
  • the stem 26 of the open/close element 12 is slidably mounted within the stretch 16 in such a way that the latter will function as guide element and as dynamic-seal element for the open/close element 12 itself: the dynamic seal is thus provided between the environment giving out into which is the first mouth 2 and the environment giving out into which is the second mouth 4.
  • the axial length of the stem 26 is chosen in such a way that it will extend along the stretch 16 as far as the holes that define the mouth 2, which thus occupy a position corresponding to the neck 28 that provides substantially an annular fluid chamber.
  • the head 30 is positioned practically entirely within the stretch 18, except for a small surface portion 32 that projects within the stretch 16 beyond the shoulder 19.
  • the head 30 has a diameter greater than the diameter D16 but smaller than the diameter D18, so that provided in a position corresponding to the shoulder 19 is a first contrast seat A1 for the open/close element 12, in particular for the conical surface 32.
  • annular chamfer is made that increases the area of contact with the conical surface 32 at the same time reducing the specific pressure developed at the contact therewith, hence minimizing the risks of damage to the surface 32. It in any case important for the seal diameter between the open/close element 12 and the shoulder 19 to be substantially the same as the diameter D16.
  • a first threaded recess 36 engaged in which is a bushing 38 having a through guide hole 40 sharing the axis H.
  • the diameter of the hole 40 is equal to the diameter D35 for reasons that will emerge more clearly from the ensuing description.
  • the bushing 38 comprises a castellated end portion 42, which functions as contrast element for a spacer ring 44.
  • the spacer ring 44 offers in turn a contrast surface to the head 30 of the open/close element 12, in particular to the collar 34.
  • the choice of the thickness of the spacer ring 44 enables adjustment of the stroke of the open/close element 12 and hence of the area of passage between the mouth 2 and the mouth 6.
  • a second threaded recess 46 is engaged in which is a ringnut 48.
  • the ringnut 48 functions as contrast for a ring 50, which in turn offers a contrast surface for a first elastic-return element 52 housed in the cylindrical recess 27.
  • the ringnut 48 is screwed within the threaded recess 46 until it comes to bear upon the shoulder between the latter and the jacket 10: in this way, the adjustment of the pre-load applied to the elastic-return element 52 is determined by the thickness (i.e., by the band width) of the ring 50.
  • the second open/close element 14 is set inside the stem 26 and is slidable and coaxial with respect to the first open/close element 12.
  • the open/close element 14 comprises:
  • the geometry of the castellated end 42 contributes to providing, by co-operating with the holes 34a, a passageway for the flow of fluid that is sent on through the section of passage defined between the conical surface 60 and the contrast seat A2 towards the second mouth 4.
  • the cup-shaped end portion 64 has an outer diameter D64 equal to the diameter of the hole 40 and comprises a recess that constitutes the outlet of a central blind hole 66 provided in the stem 56.
  • the hole 66 intersects a first set of radial holes and a second set of radial holes, designated, respectively, by the reference numbers 68, 70.
  • the two sets each comprise four radial holes 68, 70 set at the same angular distance apart.
  • the position of the aforesaid sets of radial holes is such that the holes 68 are located substantially in a position corresponding to the cylindrical recess 35, whilst the holes 70 are located substantially in a position corresponding to the cylindrical recess 27.
  • Coupling between the cup-shaped end portion 64 (having a diameter D64) and the hole 40 (having a diameter substantially equal to the diameter D64) provides a dynamic seal between the open/close element 14 and the bushing 38: this seal separates the environment giving out into which is the third mouth 6 from the environment giving out into which is the second mouth 4.
  • the hydraulic consumption depends not only upon the temperature and the type of fluid, but also upon the difference in pressure existing between the environments giving out into which are the mouths 2 and 4, upon the diametral clearance, upon the length of the coupling between the cup-shaped end portion 64 and the bushing 38, and upon other parameters such as the geometrical tolerances and the surface finish of the various components.
  • the hydraulic consumptions of the two dynamic seals add up and define the total hydraulic consumption of the solenoid valve 1.
  • an anchor 71 provided for co-operating with the solenoid 8, which has a reference position defined by a half-ring 72 housed in an annular groove on the shank 54; advantageously, the anchor 71 can be provided as a disk comprising notches with the dual function of lightening the overall weight thereof and of reducing onset of parasitic currents.
  • a collar 73 inserted within which is a cup 74, blocked on the collar 73 by means of a threaded ringnut 76 that engages an outer threading made on the collar 73.
  • a toroid 78 housing the solenoid 8, which is wound on a reel 80 housed in an annular recess of the toroid 78 itself.
  • the toroid 78 is traversed by a through hole 79 sharing the axis H and is surmounted by a plug 82 bearing thereon and blocked on the cup 74 by means of a cap 84 bearing a seat for an electrical connector 85 and electrical connections (not visible) that connect the electrical connector to the solenoid 8.
  • the toroid 78 comprises a first base surface, giving out on which is the annular recess 79, which offers a contrast to the anchor 71, determining the maximum axial travel thereof (i.e., the stroke), designated by c.
  • the maximum axial travel of the anchor 71 is hence determined by subtracting the thickness of the anchor 71 itself (i.e., the band width thereof) from the distance between the first base surface of the toroid 78 and the ringnut 48.
  • a first adjustment shim R1 is provided, preferably provided as a ring having a calibrated thickness; alternatively, it is possible to replace the anchor 71 with an anchor of a different thickness.
  • the stroke c of the anchor 71 is hence constituted by three components:
  • the plug 82 comprises a through hole 84 sharing the axis H and comprising a first stretch and a second stretch with widened diameter 86, 88 at opposite ends thereof. It should be noted that the through hole 84 enables, by means of introduction of a measuring instrument, verification of the displacements of the open/close element 14 during assemblage of the solenoid valve 1.
  • the stretch 86 communicates with the hole 79 and defines therewith a single cavity set inside which is a second elastic-return element 90, co-operating with the second open/close element 14.
  • the elastic-return element 90 bears at one end upon a shoulder made on the shank 54 and at another end upon a second adjustment shim R2 bearing upon a shoulder created by the widening of diameter of the stretch 86.
  • the adjustment shim R2 has the function of adjustment of the pre-load of the elastic element 90.
  • Forced in the stretch 88 is a ball 92 that isolates the hole 84 with respect to the environment, preventing accidental exit of liquid.
  • the solenoid valve 1 is inserted in an oleodynamic circuit in such a way that each of the mouths 2, 4, 6 is hydraulically connected to a corresponding environment, each having its own level of pressure - respectively p 2 , p 4 , p 6 - and being such that p 2 > p 6 > p 4 .
  • Figure 1C shows a single-line diagram that illustrates the solenoid valve 1 in a generic operating position: it should be noted how arranged between the first mouth 2 and the second mouth 4 are two flow restrictors with variable cross section A1 and A2, which represent schematically the passage ports provided by the first and second open/close elements.
  • the value of the pressure is equal to that at the third mouth 6 but for the pressure drops along the branch 6-6'.
  • the flow restrictor A2 which represents schematically the action of the second open/close element 14.
  • the flow restrictor with variable cross section A1 which represents schematically the action of the first open/close element 12.
  • Figure 1A illustrates the first operating position P1 of the solenoid valve 1, in which the first and second open/close elements 12, 14 are in the resting position. This means that no current traverses the solenoid 8 and no action is exerted on the anchor 71, so that the open/close elements 12, 14 are kept in position by the respective elastic-return elements 52, 90.
  • the first open/close element 12 is kept bearing upon the ring 44 by the first elastic-return element 52, whilst the second open/close element 14 is kept in position thanks to the anchor 71: the second elastic-return element 90 develops its own action on the shank 54, and said action is transmitted to the anchor 71 by the half ring 72, bringing the anchor 71 to bear upon the ringnut 48.
  • the fluid can invade the cylindrical recess 35 and pass through the holes 68, invading the cup-shaped end portion 64 and coming out through the hole 40; it should be noted that the pressure that is set up in the volume of the cylindrical recess 35 is slightly higher than the value p 4 by virtue of the head losses due to traversal of the holes 68. Finally, it should be noted that the open/close element 12 itself and the guide bushing 38 define the second mouth 4.
  • FIGs of Figures 4A, 4B and 4C represent the time plots of various operating quantities of the solenoid valve 1, observed in particular during a time interval in which two events of switching of the operating position of the solenoid valve 1 occur.
  • the diagram of Figure 4A illustrates the time plot of a current of energization of the solenoid 8
  • the diagram of Figure 4B illustrates the time plot of the area of passage for the fluid offered by the sections of passage created by the open/close elements 12, 14 co-operating with the respective contrast seats A1, A2,
  • the diagram of Figure 4C illustrates the plot of the (partial) absolute displacements h 12 , h 14 of the open/close elements 12, 14, having assumed as reference (zero displacement) the resting position of each of them.
  • the reference h TOT indicates the overall displacement of the open/close element 14, equal to the sum of the displacement h 12 and of the partial displacement h 14 .
  • the second open/close element 14 defines with the contrast seat A2 a gap having area of passage S2 whereas the first open/close element 12 defines with the contrast seat A1 a gap having area of passage S1, which in this embodiment is smaller than the area S2.
  • the function of dividing the total stroke h tot into the two fractions ⁇ h 12 and ⁇ h 14 is entrusted to the shim 44.
  • the operating position P2 is activated following upon a first event of switching of the solenoid valve 1 that occurs at an instant t 1 in which an energization current of intensity I 1 is supplied to the solenoid 8.
  • the intensity I 1 is chosen in such a way that the action of attraction exerted by the solenoid 8 on the anchor 71 will be such as to overcome the force developed by the elastic-return element 90 alone.
  • the solenoid 8 is actuated for impressing on the second open/close element a first movement ⁇ h 14 in an axial direction H having a sense indicated by C in Figure 2 whereby the second open/close element, in particular the conical surface 60, is brought into contact with the second contrast seat A2 disabling the passage of fluid from the first mouth 2 to the second mouth 4, and hence providing a transition from the first operating position P1 to the second operating position P2.
  • the open/close element 14 (as likewise the open/close element 12, see the ensuing description) is moreover hydraulically balanced; consequently, it is substantially insensitive to the values of pressure with which the solenoid valve 1 operates.
  • each of the open/close elements 12, 14 is meant that the resultant in the axial direction (i.e., along the axis H) of the forces of pressure acting on the open/close element is zero. This is due to the choice of the surfaces of influence on which the action of the pressurized fluid is exerted and of the dynamic-seal diameters (in this case also guide diameters) of the open/close elements.
  • the dynamic-seal diameter of the open/close element 14 is the diameter D64, which is identical to the diameter D35 of the cylindrical recess 35, which determines the seal surface of the open/close element 14 in a region corresponding to the contrast seat A2 provided on the open/close element 12.
  • the dynamic-seal diameter is the diameter D16, which is equal to the diameter of the stem 26 (but for the necessary radial plays) and coincides with the diameter of the contrast seat A1, provided on the jacket 10, which determines the surface of influence of the open/close element 12.
  • the solenoid valve 1 in such a way that the diameters D64 and D35 associated to the open/close element 14 are substantially equal to the diameter D16 and to the diameter of the seat A1 of the open/close element 12.
  • FIG. 3A-3B The configuration of the open/close elements 12, 14 in the third operating position P3 is illustrated in Figures 3A-3B .
  • a command is issued for an increase in the energization current that traverses the solenoid 8, which brings the intensity thereof from the value I 1 (kept throughout the time that elapses between t 1 and t 2 ) to a value I 2 > I 1 .
  • ABS anti-lock braking system
  • the solenoid valve 1 which in the embodiment described is of the so-called “cartridge” type, is inserted into a body 100 - which functions as connection element - communicating with a first environment, a second environment, and a third environment designated by the references VC, V1, V2.
  • the environments VC, V1, V2 are, respectively, at a level of pressure p MAX (or control pressure), p INT (intermediate pressure), and psc (exhaust pressure), lower than the intermediate pressure P INT .
  • the solenoid valve 1 is inserted in the body 100 in a seat 102 in which there is a separation of the levels of pressure associated to the individual environments by means of three gaskets of an O-ring type housed, respectively, in the annular grooves 20, 22 and 24 and designated, respectively, by the reference numbers 104, 106, 108.
  • the O-ring 104 guarantees an action of seal in regard to the body across the environments V2 V1
  • the O-ring 106 guarantees an action of seal in regard to the body across the environments V1 and VC.
  • the last O-ring designated by the reference number 108, exerts an action of seal that prevents any possible leakage of fluid on the outside of the body.
  • the environment VC at pressure p MAX is a control volume of a braking system set on a hydraulic power line that hydraulically connects a braking-liquid pump 110 to a cylinder 112 of a brake calliper 114, here represented as being of a floating type but the same applies to callipers of a fixed type.
  • the calliper 114 exerts its own action on a disk 116, connected in rotation to the wheel of a vehicle.
  • the control volume VC is hydraulically connected to the inlet mouth 2 of the solenoid valve 1, whilst connected to the second and third mouths 4, 6 of the solenoid valve 1 are the environments V2 and V1, respectively, where the environment V1 is functionally a further control volume kept at a level of pressure lower than the pressure p MAX that obtains in the control volume VC during braking, whilst the environment V2 coincides with an exhaust environment, in which the relative pressure is substantially zero.
  • control volume VC is pressurized - during a braking action - by the action of the user, who via the hydraulic pump 110 sends pressurized fluid to the cylinder 112 causing gripping of the calliper 114 on the disk 116.
  • the solenoid valve 1 is kept in the operating position P3, which is equivalent to a completely traditional operation of the braking system of the vehicle.
  • the pressure that is set up in the control volume VC is equal to the pressure of the fluid in the cylinder 112 during braking, whereas the value of intermediate pressure p int is modulated by means of an electronic control unit operatively connected to a regulation device (neither of which are illustrated in Figure 5B ), as a function of the boundary conditions detected by sensors in themselves known, such as, for example, icy, wet, or damp, road surface, the type of asphalt or else again the temperature of the disks 116.
  • the system intervenes and performs its own function by exploiting the switching of the operating positions of the solenoid valve 1 to modulate the braking action.
  • the solenoid valve 1 is switched into the position P1 in the case where a control unit of the ABS determines the need for a practically total release of the braking action on the disk 116 or when the braking action impressed by the user ceases.
  • control volume VC and consequently the cylinder 112
  • the control volume VC would be hydraulically connected to the environment V2, thus setting it in the discharging condition.
  • the electromagnet 8 is controlled so as to switch the solenoid valve into the operating position P2, in which the control volume VC is hydraulically connected to the volume at intermediate pressure V1 and is isolated from the exhaust environment V2.
  • control volume VC is depressurized, causing a partial release of the action on the disk 116.
  • the solenoid 8 is governed so as to switch the solenoid valve again into the position P3.
  • the application of the solenoid valve 1 to a braking system entails a second advantage: in fact, for what has been described previously, it is not possible to make a direct switching from the operating position P3 to the operating position P1, which imposes on the solenoid valve to assume, albeit for an extremely short time interval, the operating position P2. This results in a more gradual deceleration during release of the brake.
  • the seals between the open/close elements 12, 14 and the respective contrast seats A1, A2 can be provided by means of the contact of two conical surfaces, where the second conical surface replaces the sharp edges of the shoulders on which the contrast seats are provided.
  • the rings can be of a self-lubricating type, hence with a low coefficient of friction, so as not to introduce high forces of friction and not to preclude operation of the valve itself.
  • Figure 6 illustrates, by way of example, an embodiment of the solenoid valve 1 that envisages use of dynamic-seal rings designated by the reference number 130.
  • the environment connected to the first mouth 2 and the environment connected to the second mouth 4 will be set in the discharging condition towards the environment connected to the third mouth 6 and the leakages of fluid will have a direction such as to flow from the environment connected to the mouth 4 to the environment connected to the mouth 6.
  • the solenoid valve 1 By switching the solenoid valve 1 from the operating position P1 to the operating position P2, the environment connected to the second mouth 4 is excluded, while there remains only the hydraulic connection of the inlet environment connected to the first mouth 2 with the mouth 6, i.e., with the exhaust: as compared to the previous operating position, the flowrate measured at outlet from the mouth 6 will be lower than in the previous case, since the contribution of the flow from the mouth 4 to the mouth 6 ceases.
  • the inventors have moreover noted that it is particularly advantageous to connect the mouths 2, 4, 6 of the solenoid valve 1 between environments with pressure levels that are different again from the cases described.
  • the mouth 6 is the first mouth and the mouths 4, 2 are the second and third mouths, respectively. At times the correspondence will be explicitly indicated in brackets in the text, where necessary.
  • the solenoid valve 1 induces lower head losses in the current fluid that traverses it and proceeds from the mouth 6 to the mouths 2 and 4.
  • Figure 7 illustrates a second embodiment of a solenoid valve according to the invention and designated by the reference number 200.
  • the solenoid valve 200 comprises a first mouth 202 for inlet of a working fluid, and a second mouth 204 and a third mouth 206 for outlet of said working fluid.
  • the solenoid valve 200 can assume the three operating positions P1, P2, P3 previously described, establishing the hydraulic connection between the mouths 202, 204 and 206 as has been described previously. This means that in the position P1 a passage of fluid from the first mouth 202 to the second mouth 204 and the third mouth 206 is enabled, in the position P2 a passage of fluid from the first mouth 202 to the third mouth 206 is enabled, whilst the passage of fluid from the mouth 202 to the mouth 204 is disabled; finally, in the position P3 the passage of fluid from the mouth 202 to the mouths 204 and 206 is completely disabled.
  • An electromagnet 208 comprising a solenoid 208a can be driven for causing a switching of the operating positions P1, P2, P3 of the solenoid valve 200, as will be described in detail hereinafter.
  • the solenoid valve 200 comprises a plurality of components coaxial with one another and sharing a main axis H'.
  • the solenoid valve 200 comprises a jacket 210 housed in which are a first open/close element 212 and a second open/close element 214 and fixed on which is the solenoid 208a, carried by a supporting bushing 209.
  • the jacket 210 is traversed by a through hole sharing the axis H' and comprising a first stretch 216 having a diameter D216 and a second stretch 218 comprising a diameter D218, where the diameter D218 is greater than the diameter D216.
  • a shoulder 219 is thus created.
  • the mouths 202, 206 are provided by means of through holes with radial orientation made, respectively, in a position corresponding to the stretch 216 and to the stretch 218 and in communication therewith.
  • first annular groove 220 a first annular groove 220, a second annular groove 222, and a third annular groove 224, each designed to receive a gasket of the O-ring type, arranged on opposite sides with respect to the radial holes that define the mouth 202 and the radial holes that define the mouth 206.
  • the mouth 206 is comprised between the grooves 222 and 224 whilst the mouth 2 is comprised between the grooves 220 and 222.
  • the three annular grooves 220, 222, 224 are provided with the same seal diameter so as to minimize the unbalancing induced by the resultant of the forces of pressure acting on the outer surface of the jacket 210, which otherwise would be such as to jeopardize fixing of the jacket of the solenoid valve in the corresponding seat provided on a component or in an oleodynamic circuit where it is installed.
  • the first open/close element 212 is basically configured as a hollow tubular element comprising a stem 226 - which is hollow and provided in which is a first cylindrical recess 227 -, a neck 228, and a head 230, which has a conical contrast surface 232 and a collar 234.
  • the neck 228 has a diameter smaller than the stem 226.
  • a ring of axial holes 234A preferably provided in the collar 234 is a ring of axial holes 234A, whilst a second cylindrical recess 235 having a diameter D235 is provided in the head 230.
  • the stem 226 of the open/close element 212 is slidably mounted within the stretch 216, in such a way that the latter will function as guide element and as dynamic-seal element for the open/close element 212 itself: the dynamic seal is thus provided between the environment giving out into which is the first mouth 202 and the environment giving out into which is the second mouth 4. As has been described previously, this, however, gives rise to slight leakages of fluid through the gaps existing between the open/close element 212 and the stretch 216, contributing to defining the hydraulic consumption of the solenoid valve 200.
  • the axial length of the stem 226 is chosen in such a way that it will extend along the stretch 216 as far as the holes that define the mouth 202, which are thus in a position corresponding to the neck 228 that provides substantially an annular fluid chamber.
  • the head 230 is positioned practically entirely within the stretch 218, except for a small surface portion 232 that projects inside the stretch 216 beyond the shoulder 219.
  • the head 230 has a diameter greater than the diameter D216 but smaller than the diameter D218 so that provided in a position corresponding to the shoulder 19 is a first contrast seat A1' for the open/close element 212, in particular for the conical surface 232.
  • a first threaded recess 236 engaged in which is a bushing 238 comprising a plurality of holes that define the mouth 204. Some of said holes have a radial orientation, whilst one of them is set sharing the axis H'.
  • the bushing 238 houses a spacer ring 240, fixed with respect to the first open/close element 212, bearing upon which is a first elastic-return element 242 housed within the recess 227.
  • the choice of the band width of the spacer ring 240 enables adjustment of the pre-load of the elastic element 242.
  • Fixed at the opposite end of the jacket 210 is a second bushing 244 having a neck 246 fitted on which is the supporting bushing 209.
  • the bushing 244 constitutes a portion of the magnetic core of the electromagnet 8 and offers a contrast surface to a spacer ring 248 that enables adjustment of the stroke of the first open/close element 212 and functions as contrast surface for the latter against the action of the elastic element 242.
  • the bushing 238 functions as contrast for the elastic element 242 in so far as the elastic forces resulting from the deformation of the elastic element are discharged thereon.
  • the second open/close element 214 is set practically entirely within the bushing 244.
  • the latter comprises a central through hole 250 that gives out into a cylindrical recess 252, facing the open/close element 212.
  • the open/close element 214 comprises a stem 254 that bears upon a head 256, both of which are coaxial to one another and are set sharing the axis H', where the stem 254 is slidably mounted within the hole 250, whilst the head 256 is slidably mounted within the recess 252.
  • the stem 254 simply bears upon the head 256 since - as will emerge more clearly - during operation it exerts an action of thrust (and not of pull) on the head 256, but in other embodiments a rigid connection between the stem 254 and the head 256 is envisaged.
  • the stem 254 is, instead, rigidly connected to the anchor 264.
  • the head 256 further comprises a conical contrast surface 258 designed to co-operate with a second contrast seat A2' defined by the internal edge of the recess 235.
  • a spacer ring 260 Set between the head 256 and the bottom of the recess 252 is a spacer ring 260, the band width of which determines the stroke of the second open/close element 214.
  • the spacer ring 260 offers a contrast surface to the open/close element 214, in particular to the head 256, in regard to the return action developed by a second elastic-return element 262, bearing at one end upon the head 256 and at another end upon the bushing 238.
  • the elastic element 262 is set sharing the axis H' and inside the elastic element 242.
  • the stem 254 is rigidly connected to an anchor 264 of the electromagnet 208 that bears upon a spring 266 used as positioning element.
  • the maximum travel of the anchor 266 is designated by c'.
  • the stroke of the anchor 266 is chosen so as to be equal to or greater than the maximum displacement allowed for the open/close element 214.
  • part of the fluid In traversing the first gap, part of the fluid can come out through the holes that define the third mouth 206, whereas another part of the fluid traverses the holes 234a and proceeds towards the second gap.
  • the solenoid valve 200 To switch the solenoid valve 200 from the position P1 to the position P2, it is sufficient to control the electromagnet 208 so that it impresses on the second open/close element 214 a first movement that brings the latter, in particular the conical surface 258, to bear upon the second contrast seat A2', disabling fluid communication between the first mouth 202 and the second mouth 204.
  • the open/close element 214 In a way similar to the open/close element 14, the open/close element 214 is hydraulically balanced because the seal diameter, coinciding with the diameter D235 of the contrast seat A2', is substantially equal to the guide diameter, i.e., the diameter of the recess 252.
  • the aforesaid first movement is imparted to the open/close element 214 by means of circulation, in the solenoid 208a, of a current having an intensity I 1 sufficient to displace the anchor 264 of just the distance necessary to bring the open/close element to bear upon the seat A2' and to overcome the resistance of just the elastic element 262.
  • the open/close element 214 is hydraulically balanced since the seal diameter, i.e., the diameter of the contrast seat A2', is equal to the diameter of the recess 252 in which the head 256 is guided and slidably mounted.
  • the second open/close element 214 remains in contact against the first open/close element 212 keeping the hydraulic connection between the mouths 202 and 206 closed.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Electromagnetism (AREA)
  • Fluid Mechanics (AREA)
  • Transportation (AREA)
  • Magnetically Actuated Valves (AREA)

Claims (17)

  1. Electrovanne (1 ; 200) comprenant trois bouches (2, 4, 6 ; 202, 204, 206) et trois positions opérationnelles (P1, P2, P3), dans laquelle lesdites trois bouches (2, 4, 6 ; 202, 204, 206) comprennent :
    une première bouche (2 ; 202) pour l'entrée d'un fluide de travail ;
    une deuxième bouche (4 ; 204) et une troisième bouche (6 ; 206) pour la sortie du fluide de travail,
    et dans laquelle lesdites trois positions opérationnelles (P1, P2, P3) comprennent :
    une première position opérationnelle (P1), dans laquelle un passage de fluide de ladite première bouche (2 ; 202) auxdites deuxième bouche (4 ; 204) et troisième bouche (6 ; 206) est autorisé,
    une deuxième position opérationnelle (P2), dans laquelle un passage de fluide de ladite première bouche (2 ; 202) vers une seule (6 ; 206) desdites deuxième et troisième bouches (4, 6) est autorisé, et
    une troisième position opérationnelle (P3) dans laquelle le passage de fluide de la première bouche (2 ; 202) à la deuxième bouche (4 ; 204) et la troisième bouche (6 ; 206) n'est pas autorisé,
    ladite électrovanne (1 ; 200) comprenant en outre un électroaimant (8 ; 208) qui peut être commandé pour provoquer une commutation de la position opérationnelle (P1, P2, P3), et
    un premier élément d'ouverture/fermeture (12 ; 212) et un second élément d'ouverture/fermeture (14 ; 214) coopérant, respectivement, avec un premier siège de butée (A1 ; A1') et un second siège de butée (A2 ; A2'), dans laquelle ledit premier élément d'ouverture/fermeture (12 ; 212) et ledit premier siège de butée (A1 ; A1') sont prévus pour commander le passage de fluide de ladite première bouche (2 ; 202) à ladite troisième bouche (6 ; 206), et dans laquelle ledit second élément d'ouverture/fermeture (14 ; 214) et ledit second siège de butée (A2 ; A2') sont prévus pour la régulation du passage de fluide de ladite première bouche (2 ; 202) à ladite deuxième bouche (4 ; 204), l'électrovanne (1 ; 200) étant caractérisée en ce que :
    ledit solénoïde (8 ; 208) peut être actionné pour imprimer sur ledit second élément d'ouverture/fermeture (14 ; 214) :
    un premier mouvement, moyennant quoi ledit second élément d'ouverture/fermeture (14 ; 214) est amené en contact avec ledit second siège de butée (A2 ; A2') ne permettant pas le passage de fluide de ladite première bouche (2 ; 202) à ladite deuxième bouche (4 ; 204) fournissant une commutation de ladite première position opérationnelle (P1) à ladite deuxième position opérationnelle (P2),
    un second mouvement, suite audit premier mouvement, moyennant quoi ledit second élément d'ouverture/fermeture (14 ; 214) déplace ledit premier élément d'ouverture/fermeture (12 ; 22) contre ledit premier siège de butée (A1 ; A1') ne permettant pas le passage de fluide de ladite première bouche (2 ; 202) à ladite troisième bouche (6 ; 206) et fournissant une commutation de ladite deuxième position opérationnelle (P2) à ladite troisième position opérationnelle (P3),
    dans laquelle, pendant ledit second mouvement, ledit second élément d'ouverture/fermeture (14 ; 214) est en contact avec ledit second siège de butée (A2 ; A2'), et
    dans laquelle, de plus, ledit premier élément d'ouverture/fermeture (12 ; 212) et ledit second élément d'ouverture/fermeture (14 ; 214) sont coaxiaux (H) l'un par rapport à l'autre et hydrauliquement équilibrés.
  2. Electrovanne (1 ; 200) selon la revendication 1, caractérisée en ce qu'elle comprend une chemise (10 ; 210) montée de manière coulissante, à l'intérieur de laquelle se trouve ledit premier élément d'ouverture/fermeture (12 ; 212), dans laquelle ladite première bouche (2 ; 202), la deuxième bouche (4 ; 204) et la troisième bouche (6 ; 206) de ladite électrovanne (1 ; 200) sont prévues sur ladite chemise (10 ; 210) et dans laquelle, de plus, ladite première surface de butée (A1 ; A1') est prévue sur ladite chemise (10 ; 210) et ladite seconde surface de butée (A2 ; A2') est prévue sur ledit premier élément d'ouverture/fermeture (12 ; 212).
  3. Electrovanne (1 ; 200) selon la revendication 2, caractérisée en ce que ladite chemise (10 ; 210) est traversée par un trou de passage comprenant une première portion (16 ; 216) et une seconde portion (18 ; 218), dans laquelle ladite première portion (16 ; 216) a un diamètre (D16, D216) inférieur à un diamètre (D18 ; D218) à ladite deuxième portion (18 ; 218), et
    en ce que ledit premier élément d'ouverture/fermeture (12 ; 212) comprend une tige (26 ; 226) montée de manière coulissante et guidée dans ladite première portion (16 ; 216) et une tête (30 ; 230) comprenant une surface de butée conique (32 ; 232) conçue pour coopérer avec ledit premier siège de butée (A1 ; A1'), ledit premier siège de butée (A1 ; A1') étant prévu dans une zone correspondant à un épaulement (19 ; 219) entre ladite première portion (16 ; 216) et ladite première portion (18 ; 218).
  4. Electrovanne (1 ; 200) selon la revendication 3, caractérisée en ce que ladite tige (26 ; 226) a un diamètre égal à un diamètre dudit premier siège de butée (A1 ; A1').
  5. Electrovanne (1 ; 200) selon la revendication 4, caractérisée en ce que la tête (30 ; 230) dudit premier élément d'ouverture/fermeture (12 ; 212) comprend un évidement cylindrique (35 ; 235) qui fournit ledit second siège de butée (A2 ; A2') pour ledit second élément d'ouverture/fermeture (14 ; 214).
  6. Electrovanne selon la revendication 5, caractérisée en ce que la tige (26 ; 226) dudit premier élément d'ouverture/fermeture (12 ; 212) comprend un autre évidement cylindrique (27 ; 227), dans lequel est logé un premier élément élastique de rappel (52 ; 242) conçu pour coopérer avec ledit premier élément d'ouverture/fermeture (12 ; 212), ledit premier élément élastique de rappel venant de plus en butée contre une bague d'espacement (50 ; 240) fixée par rapport audit premier élément d'ouverture/fermeture (12 ; 212).
  7. Electrovanne (1) selon l'une quelconque des revendications 2 à 6, caractérisée en ce que ledit second élément d'ouverture/fermeture (14) est placé à l'intérieur dudit premier élément d'ouverture/fermeture (12) et est mobile par rapport à ce dernier.
  8. Electrovanne (1) selon la revendication 7, caractérisée en ce que ledit second élément d'ouverture/fermeture (12) comprend :
    une tige terminale (54) placée au niveau de sa première extrémité, à laquelle est lié un ancrage (71) coopérant avec ledit solénoïde (8),
    une tête (58) ayant une surface de butée conique (60) conçue pour entrer en contact avec ledit second siège de butée (A2) et placée au niveau de sa seconde extrémité, et
    une tige (56) placée entre et raccordant ladite tige (54) et ladite tête (58).
  9. Electrovanne (1) selon la revendication 8, caractérisée en ce que la tige (56) dudit second élément d'ouverture/fermeture (14) comprend un trou coaxial par rapport à ce dernier intersecté par un premier ensemble de trous radiaux (68) et un second ensemble de trous radiaux (70), ledit premier ensemble de trous radiaux étant en communication de fluide avec ladite deuxième bouche (4) de ladite électrovanne (1).
  10. Electrovanne (1) selon l'une quelconque des revendications 8 à 9, caractérisée en ce que la tête (58, 64) dudit second élément d'ouverture/fermeture (12) est guidée dans un trou de passage central (40) d'une douille de guidage (38) placée au niveau d'une second extrémité de ladite chemise (10), ladite douille de guidage (38) et la tête (12) dudit second élément d'ouverture/fermeture (12) définissant ladite deuxième bouche (4) de ladite électrovanne (1).
  11. Electrovanne (1) selon la revendication 10, caractérisée en ce que le trou de passage central (40) de ladite douille de guidage (38) a un diamètre (D64) égal à un diamètre (D35) dudit second siège de butée (A2).
  12. Electrovanne (1) selon l'une quelconque des revendications 8 à 11, caractérisée en ce qu'elle comprend un second élément élastique de rappel (90) conçu pour coopérer avec ledit second élément d'ouverture/fermeture (14).
  13. Electrovanne (1) selon la revendication 12, caractérisée en ce qu'elle comprend une bague (74) liée à ladite chemise (10) dans une position correspondant à ladite première extrémité et logeant ledit solénoïde (8), placé dans un évidement annulaire à l'intérieur d'un tore (78) et un bouchon (82) s'appuyant sur ledit tore (78) et lié à ladite bague (74), dans ledit bouchon (82) et ledit tore (78), étant définie une cavité à l'intérieur de laquelle est logé ledit second élément élastique de rappel (90).
  14. Electrovanne (200) selon la revendication 6, caractérisée en ce que ladite chemise (210) comprend une première douille (238) et une seconde douille (244), fixées, respectivement, au niveau de leur première extrémité et de leur seconde extrémité, dans laquelle ladite première douille (238) comprend une pluralité de trous (204) définissant ladite deuxième bouche et définit une butée pour ledit premier élément élastique de rappel (242) associé audit premier élément d'ouverture/fermeture (212) et pour un second élément élastique de rappel (262) associé audit second élément d'ouverture/fermeture (214).
  15. Electrovanne (200) selon la revendication 14, caractérisée en ce que ledit second élément d'ouverture/fermeture comprend une tête (256) montée de manière coulissante dans un évidement cylindrique (252) prévu dans ladite seconde douille (244) et une tige (250) montée de manière coulissante dans ladite seconde douille (244).
  16. Electrovanne (200) selon la revendication 15, caractérisée en ce que le second siège de butée (A2') a un diamètre égal à un diamètre dudit évidement cylindrique (252) de ladite seconde douille (244).
  17. Electrovanne (200) selon la revendication 15 ou la revendication 16, caractérisée en ce que ledit électroaimant (208) comprend un ancrage (264) raccordé à la tige dudit second élément d'ouverture/fermeture et logé dans une douille de support (209) pour un solénoïde (208a) dudit électroaimant fixé sur ladite seconde douille (244).
EP20110190645 2011-11-24 2011-11-24 Électrovanne Active EP2597343B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP20110190645 EP2597343B1 (fr) 2011-11-24 2011-11-24 Électrovanne
US13/591,816 US8851118B2 (en) 2011-11-24 2012-08-22 Solenoid valve

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP20110190645 EP2597343B1 (fr) 2011-11-24 2011-11-24 Électrovanne

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EP2597343B1 true EP2597343B1 (fr) 2013-11-20

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Publication number Priority date Publication date Assignee Title
EP2796675B1 (fr) * 2013-04-26 2016-11-23 C.R.F. Società Consortile per Azioni Moteur à combustion interne avec un système de distribution variable des soupapes d'admission avec électrovannes à trois voies et méthode de contrôle de ce moteur selon un mode à "levée unique"
EP2806195B1 (fr) 2013-05-22 2015-10-28 C.R.F. Società Consortile per Azioni Soupape de commande à trois positions et à trois voies comportant un actionneur piézoélectrique ou magnétostrictif et système d'injection de carburant comprenant cette soupape
EP2832960B1 (fr) * 2013-08-01 2015-09-16 C.R.F. Società Consortile per Azioni Moteur à combustion interne à commande de soupapes d'admission variable avec une vanne électrique de contrôle à deux voies et trois positions
JP2021173354A (ja) * 2020-04-27 2021-11-01 川崎重工業株式会社 弁装置

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Publication number Priority date Publication date Assignee Title
JPS62196481A (ja) * 1986-02-21 1987-08-29 Nippon Denso Co Ltd 電磁弁
US5918630A (en) * 1998-01-22 1999-07-06 Cummins Engine Company, Inc. Pin-within-a-sleeve three-way solenoid valve with side load reduction
IT1309954B1 (it) * 1999-12-30 2002-02-05 Lucio Berto Struttura di valvola di sicurezza particolarmente per gas.

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EP2597343A1 (fr) 2013-05-29
US20130134337A1 (en) 2013-05-30
US8851118B2 (en) 2014-10-07

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